US9506376B2 - Fossil-fired steam generator - Google Patents

Fossil-fired steam generator Download PDF

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Publication number
US9506376B2
US9506376B2 US13/877,729 US201113877729A US9506376B2 US 9506376 B2 US9506376 B2 US 9506376B2 US 201113877729 A US201113877729 A US 201113877729A US 9506376 B2 US9506376 B2 US 9506376B2
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Prior art keywords
fossil
pressure
flow medium
supply line
steam generator
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Expired - Fee Related, expires
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US13/877,729
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English (en)
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US20130205785A1 (en
Inventor
Martin Effert
Frank Thomas
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Siemens Energy Global GmbH and Co KG
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Siemens AG
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Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: EFFERT, MARK, THOMAS, FRANK
Publication of US20130205785A1 publication Critical patent/US20130205785A1/en
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Assigned to Siemens Energy Global GmbH & Co. KG reassignment Siemens Energy Global GmbH & Co. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SIEMENS AKTIENGESELLSCHAFT
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
    • F01K7/24—Control or safety means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K21/00—Steam engine plants not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating

Definitions

  • the invention relates to a fossil-fired steam generator for a steam power station with a number of economizer, evaporator and superheater heating surfaces forming a flow path through which a flow medium M flows in a plurality of pressure stages, in which, in a high-pressure stage, an overflow line is connected to the flow path on its inlet side and leads to an injection valve disposed in the flow path upstream from a superheater heating surface in a medium-pressure stage on the flow medium side.
  • a fossil-fired steam generator generates superheated steam with the aid of heat created by the combustion of fossil fuels.
  • Fossil-fired steam generators are mostly used in steam power stations which primarily serve to generate electricity. In such power stations the steam is supplied to a steam turbine.
  • the fossil-fired steam generator also comprises a plurality of pressure stages with different thermal states of the water-steam mixture contained therein in each case.
  • the flow medium on its flow path initially flows through economizers which use residual heat to preheat the flow medium, and subsequently flows through various stages of evaporator and superheater heating surfaces.
  • the flow medium is evaporated in the evaporator, then any possible residual moisture is separated off in a separation device and remaining steam contained therein is heated up further in the superheater.
  • the superheated steam then flows into the high-pressure part of the steam turbine, is evaporated there and supplied to the following pressure stage of the steam generator. There it is superheated once more and supplied to the next pressure section of the steam turbine.
  • the heating power transferred to the superheaters can fluctuate greatly. It is therefore frequently necessary to regulate the superheating temperature. Usually this is mostly achieved both in the high-pressure stage and also in the medium-pressure stages for intermediate superheating by an injection of feed water upstream or downstream of individual superheater surfaces for cooling, i.e. an overflow line branches off from the main flow of the flow medium and leads to injection valves disposed accordingly there.
  • the injection in such cases is usually regulated via the temperature deviation from a predetermined nominal temperature value at the outlet of the superheater of the respective pressure stage.
  • Modern power plants not only demand high levels of efficiency but also a method of operation that is as flexible as possible. As well as short startup times and high load change speeds, these also include the option of compensating for frequency faults in the electricity grid. In order to fulfill these requirements the power plant must be able to provide additional power of for example 5% and more within a few seconds.
  • a permanent throttling of the turbine valves to maintain a reserve however always leads to a loss of efficiency, so that to drive the system cost-effectively, the degree of throttling should be kept as low as is absolutely necessary.
  • a number of designs of fossil-fired steam generators for example once-through steam generators under some circumstances demand a significantly lower boiler volume than for example natural boiler steam generators.
  • the difference in the size of the boiler has an influence in the method described above on the behavior during changes in power of the power station block.
  • the object of the invention is therefore to specify a fossil-fired steam generator of the type described above, in which the efficiency of the steam process is not disproportionately adversely affected. At the same time the short-term power increase is to be made possible regardless of the design of the fossil-fired steam generator without invasive structural modifications to the entire system.
  • the overflow line having two supply lines, of which the first branches before a high-pressure preheater and the second branches off on the flow medium side downstream of the high-pressure preheater.
  • the invention is based on the idea that additional injection of feed water can make a further contribution to a rapid change in performance.
  • additional injections in the area of the superheater the steam mass flow can namely be briefly increased.
  • injections are initiated in this case by reducing the nominal temperature value at the outlet of the respective pressure stage. The higher the enthalpy level of the injection water is in such cases, the more injection water mass flow is needed to achieve the new nominal temperature value required. Accordingly a comparatively larger volume of steam is produced from a higher enthalpy level of the injection water.
  • the enthalpy of the injection water being able to be regulated if necessary.
  • This is able to be achieved by the injection water tapped off downstream of a high-pressure preheater being mixed with a small amount of injection water tapped off upstream of the high-pressure preheater, so that in this way the desired enthalpy of the injection water can be set.
  • two supply lines lead respectively from the flow medium side upstream and downstream of a high-pressure preheater to the overflow line for the injection valve of the intermediate superheater.
  • the second supply line branches off on the flow medium side downstream of all high-pressure preheaters.
  • the first supply line branches off on the flow medium side upstream of all high-pressure preheaters.
  • a check valve is disposed in one of the supply lines and a throughflow regulation valve is disposed in the other supply line.
  • the medium is then mixed in an especially simple manner, on the one hand by determining the injection amount which is set by the injection regulation valve and is partly made available via the supply line with the check valve, wherein the check valve prevents a flowback from the high-pressure path into the low-pressure path.
  • the admixture of the medium of the respective other temperature is regulated via the throughflow regulation valve of the other supply line.
  • a check valve is disposed here in the first supply line and a throughflow regulation valve is disposed in the second supply line.
  • the check valve is located in the supply line with the medium of the lower temperature level.
  • the first supply line also branches off from a feed pump. Since under these circumstances the flow medium only has a comparatively higher pressure upstream from the throughflow regulation valve, it is possible in this way for the entire water path of the injection device to be at a comparatively low pressure level.
  • such an arrangement simplifies the regulation and it is further possible to use the feed pump normally used nowadays with the corresponding branch for the intermediate superheating injection since the cool medium can also be tapped off at the same point in the present case.
  • a throughflow measurement device is disposed in the flow path on the flow medium side downstream from the branching-off point of the second supply line. The amount tapped off does not then namely, under these circumstances for the injection water regulation, have to be taken into account via an additional measurement or a separate balancing.
  • a steam power station has a fossil-fired steam generator of this type.
  • the advantages obtained with the invention consist in particular of always enabling a sufficient undercooling of the injection water to be guaranteed by mixing injection water for the intermediate superheating from supply lines upstream and downstream of high-pressure preheaters, on the other hand in respect of provision of an immediate reserve for absolutely secure injection operation without steam formation, of enabling a maximum of additional power release to be realized by a correspondingly increased injection amount.
  • the load on all components involved such as injection point, heating surfaces and turbine, can be reduced since for the same amount of power released a smaller drop in temperature of the steam is to be expected.
  • circuit and the associated increase in released power by using the injection system is independent of other measures, so that throttled turbine valves can also additionally be opened for example in order to further strengthen the power increase of the steam turbine.
  • the effectiveness of the method is largely unaffected by these parallel measures.
  • FIG. 1 shows a flow-medium-side schematic of the high-pressure and medium-pressure part of a fossil-fired steam generator with optimized injection water supply
  • FIG. 2 shows a flow-medium-side schematic of the high-pressure and medium-pressure part of a fossil-fired steam generator with injection water supply in an alternate embodiment
  • FIG. 3 shows a diagram with simulation results for improving the immediate reserve of a fossil-fired steam generator by increasing the injection water enthalpy of the intermediate superheating in the upper load range
  • FIG. 4 shows a diagram with simulation results for improving the immediate reserve of a fossil-fired steam generator by increasing the injection water enthalpy of the intermediate superheating in a lower load range.
  • FIG. 1 shows the high-pressure part 2 and the medium-pressure part 4 of the fossil-fired steam generator 1 .
  • FIG. 1 represents a schematic of a part of the flow path 6 of the flow medium M.
  • the flow medium M is initially injected through a feed pump 8 into the high-pressure part 2 .
  • high-pressure preheaters 10 to an increased temperature, which for example can be operated with tapped-off steam.
  • economizer heating surfaces 12 in which usually flue gas waste heat is used for further heating of the flow medium
  • evaporator heating surfaces 14 in which the flow medium is evaporated with the aid of heat obtained from fossil fuel.
  • the spatial arrangement of the individual heating surfaces 12 , 14 in the hot gas duct is not shown and can vary.
  • the heating surfaces 12 , 14 shown can respectively represent a plurality of serially-connected heating surfaces, which however, for reasons of clarity, are not shown differentiated.
  • an injection valve 18 Disposed upstream of the superheater heating surfaces on the flow medium side is an injection valve 18 .
  • cooler and unevaporated flow medium M can be injected for regulating the outlet temperature at the outlet 20 of the medium pressure part 4 of the fossil-fired steam generator 1 .
  • the amount of flow medium M introduced into the injection valve 18 is regulated via an injection control valve 22 .
  • the flow medium M in this case is supplied via an overflow line 24 branching off upstream in the flow path 2 .
  • the injection system is designed for an on-demand increase of the enthalpy of the injection water.
  • the overflow line 24 has a first supply line 26 , which branches off directly in the feed pump 8 and supplies flow medium M at a comparatively low temperature to the overflow line 24 . This guarantees that there is always sufficient undercooling of the injection medium.
  • the first supply line 26 also includes a check valve flap 28 , which prevents a flowback of medium from the injection system.
  • the overflow line has a second supply line 30 , the throughflow of which is regulated by a throughflow regulation valve 32 .
  • the second supply line branches off downstream from all high-pressure preheaters 10 upstream of the economizer heating surfaces 12 , so that here flow medium M is introduced at a comparatively higher temperature into the overflow line 24 .
  • This achieves a significant increase in the amount of steam with a comparatively greater injection and increases the power of the downstream steam turbine.
  • the throughflow measurement device 34 here is disposed in the flow path 6 downstream of the two branching-off points of the supply lines 26 , 30 so that the amount of flow medium M tapped off does not need be taken into account here for the injection water regulation.
  • FIG. 2 shows an alternate embodiment, which essentially corresponds to FIG. 1 , however the locations of throughflow regulation valve 32 and check valve flap 28 are reversed here.
  • the first supply line 26 thus has a regulation valve 32 and the second supply line 30 a check valve flap 28 .
  • This embodiment is likewise possible, however the overall injection path is to be designed for higher pressures. Over and above this an additional branch 36 is to be provided for the first supply line 26 since, as a result of the higher pressure level, flow medium M cannot be removed at any given point of the feed pump 8 .
  • FIG. 3 shows a diagram with simulation results when the described circuit is utilized.
  • the graph plots the percentage of additional power in relation to full load 38 against the time 40 in seconds after a sudden reduction of the nominal temperature value for the temperature at the outlet 20 of the medium pressure part 4 by 20° C. at 95% load.
  • the curve 42 shows the results without heated injection fluid, i.e. in accordance with the usual system
  • the curve 44 shows the results with the connected injection system as described above. It can be seen in FIG. 2 that the maximum of curve 44 is higher than that of curve 42 . The additional power released is thus higher.
  • FIG. 4 is only slightly modified compared to FIG. 3 and shows the simulated curves 42 , 44 for 40% load, all other parameters match those of FIG. 3 , as does the meaning of curves 42 , 44 .
  • the two curves 42 , 44 have a flat shape and additionally a comparatively higher power increase approximately 60 seconds after the nominal value is changed, which falls quickly again thereafter in order to transition into the maximum of the flat curve.
  • Overall the curve 44 is higher at all times than the curve 42 . This means that a higher power release is also possible here, wherein despite the load only being 40%, a sufficient undercooling of the injected medium is guaranteed.
  • a steam power station equipped with such a fossil-fired steam generator 1 is able, via an immediate power release of the steam turbine, quickly to provide a power increase which serves to support the frequency of the electricity grid.
  • This power reserve is achieved by a double use of the injection valves as well as the usual temperature regulation also enables permanent throttling of the steam turbine valves for provision of a reserve to be reduced or even dispensed with entirely, through which an especially high efficiency is achieved during normal operation.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
US13/877,729 2010-10-05 2011-09-30 Fossil-fired steam generator Expired - Fee Related US9506376B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102010041962.1 2010-10-05
DE102010041962 2010-10-05
DE201010041962 DE102010041962B3 (de) 2010-10-05 2010-10-05 Fossil befeuerter Dampferzeuger
PCT/EP2011/067125 WO2012045677A2 (de) 2010-10-05 2011-09-30 Fossil befeuerter dampferzeuger

Publications (2)

Publication Number Publication Date
US20130205785A1 US20130205785A1 (en) 2013-08-15
US9506376B2 true US9506376B2 (en) 2016-11-29

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US13/877,729 Expired - Fee Related US9506376B2 (en) 2010-10-05 2011-09-30 Fossil-fired steam generator

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US (1) US9506376B2 (pl)
EP (1) EP2625390B1 (pl)
JP (1) JP5723013B2 (pl)
KR (1) KR101817777B1 (pl)
CN (1) CN103154443B (pl)
DE (1) DE102010041962B3 (pl)
DK (1) DK2625390T3 (pl)
PL (1) PL2625390T3 (pl)
WO (1) WO2012045677A2 (pl)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PL3990742T3 (pl) * 2019-06-25 2025-03-03 Vkr Holding A/S Izolowana próżniowo szyba zespolona z getterem oraz sposób aktywowania gettera w izolowanej próżniowo szybie zespolonej

Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3260246A (en) 1964-03-13 1966-07-12 Siemens Ag Regulating arrangement for forced flow type boiler
US3385270A (en) 1967-02-03 1968-05-28 Siemens Ag Steam power plant with forced-flow boiler system, particularly for supercritical pressure, and a superimposed circulating system
JPS5155801A (en) 1974-09-17 1976-05-17 Sulzer Ag Jokihatsuseikino setsushokukanetsumenotsukashitenagarerujokinoryushutsuondonieikyoooyobosu hoho
DE3607210A1 (de) 1986-03-05 1986-08-28 Jürgen Dipl.-Ing. Rimmelspacher (FH), 8068 Pfaffenhofen Dampferzeuger mit no(pfeil abwaerts)x(pfeil abwaerts)-minderungsanlage
JPH05118504A (ja) 1991-10-23 1993-05-14 Mitsubishi Heavy Ind Ltd 変圧貫流ボイラ
JPH06313506A (ja) 1993-04-30 1994-11-08 Babcock Hitachi Kk ボイラ過熱器スプレイ系統の切替方式
US5365730A (en) * 1990-09-21 1994-11-22 Siemens Aktiengesellschaft Combined gas and steam turbine system
JPH07293809A (ja) 1994-04-22 1995-11-10 Babcock Hitachi Kk 過熱低減器の注水制御方法および装置
DE4432960C1 (de) 1994-09-16 1995-11-30 Steinmueller Gmbh L & C Verfahren zum Betrieb eines Dampfkraftwerkes und Dampfkraftwerk
JPH08121708A (ja) 1994-10-25 1996-05-17 Babcock Hitachi Kk 再熱蒸気系減温器の注水制御装置
JPH11350921A (ja) 1998-06-05 1999-12-21 Babcock Hitachi Kk 排熱回収ボイラ
DE19849740A1 (de) 1998-10-28 2000-01-05 Siemens Ag Gas- und Dampfturbinenanlage
US6438939B1 (en) 1997-04-15 2002-08-27 Mitsubishi Heavy Industries, Ltd. Combined cycle power plant and cooling steam supply method for gas turbine therein
DE10227709A1 (de) 2001-06-25 2003-02-27 Alstom Switzerland Ltd Dampfturbinenanlage sowie Verfahren zu deren Betrieb
JP2005351576A (ja) 2004-06-11 2005-12-22 Hitachi Ltd 蒸気温度制御装置及び蒸気温度制御方法並びにこれらを用いた発電プラント
CN101368723A (zh) 2007-06-07 2009-02-18 艾默生过程管理电力和水力解决方案有限公司 锅炉系统中使用再热器变量的蒸汽温度控制

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19749452C2 (de) * 1997-11-10 2001-03-15 Siemens Ag Dampfkraftanlage

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3260246A (en) 1964-03-13 1966-07-12 Siemens Ag Regulating arrangement for forced flow type boiler
US3385270A (en) 1967-02-03 1968-05-28 Siemens Ag Steam power plant with forced-flow boiler system, particularly for supercritical pressure, and a superimposed circulating system
JPS5155801A (en) 1974-09-17 1976-05-17 Sulzer Ag Jokihatsuseikino setsushokukanetsumenotsukashitenagarerujokinoryushutsuondonieikyoooyobosu hoho
DE3607210A1 (de) 1986-03-05 1986-08-28 Jürgen Dipl.-Ing. Rimmelspacher (FH), 8068 Pfaffenhofen Dampferzeuger mit no(pfeil abwaerts)x(pfeil abwaerts)-minderungsanlage
US5365730A (en) * 1990-09-21 1994-11-22 Siemens Aktiengesellschaft Combined gas and steam turbine system
JPH05118504A (ja) 1991-10-23 1993-05-14 Mitsubishi Heavy Ind Ltd 変圧貫流ボイラ
JPH06313506A (ja) 1993-04-30 1994-11-08 Babcock Hitachi Kk ボイラ過熱器スプレイ系統の切替方式
JPH07293809A (ja) 1994-04-22 1995-11-10 Babcock Hitachi Kk 過熱低減器の注水制御方法および装置
DE4432960C1 (de) 1994-09-16 1995-11-30 Steinmueller Gmbh L & C Verfahren zum Betrieb eines Dampfkraftwerkes und Dampfkraftwerk
JPH08121708A (ja) 1994-10-25 1996-05-17 Babcock Hitachi Kk 再熱蒸気系減温器の注水制御装置
US6438939B1 (en) 1997-04-15 2002-08-27 Mitsubishi Heavy Industries, Ltd. Combined cycle power plant and cooling steam supply method for gas turbine therein
JPH11350921A (ja) 1998-06-05 1999-12-21 Babcock Hitachi Kk 排熱回収ボイラ
DE19849740A1 (de) 1998-10-28 2000-01-05 Siemens Ag Gas- und Dampfturbinenanlage
DE10227709A1 (de) 2001-06-25 2003-02-27 Alstom Switzerland Ltd Dampfturbinenanlage sowie Verfahren zu deren Betrieb
JP2005351576A (ja) 2004-06-11 2005-12-22 Hitachi Ltd 蒸気温度制御装置及び蒸気温度制御方法並びにこれらを用いた発電プラント
CN101368723A (zh) 2007-06-07 2009-02-18 艾默生过程管理电力和水力解决方案有限公司 锅炉系统中使用再热器变量的蒸汽温度控制

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Publication number Publication date
JP2013543573A (ja) 2013-12-05
US20130205785A1 (en) 2013-08-15
EP2625390A2 (de) 2013-08-14
DK2625390T3 (en) 2016-02-08
CN103154443A (zh) 2013-06-12
CN103154443B (zh) 2015-04-01
JP5723013B2 (ja) 2015-05-27
WO2012045677A2 (de) 2012-04-12
KR20130100148A (ko) 2013-09-09
EP2625390B1 (de) 2015-10-28
KR101817777B1 (ko) 2018-02-21
PL2625390T3 (pl) 2016-04-29
WO2012045677A3 (de) 2013-01-17
DE102010041962B3 (de) 2012-02-16

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